EP0827893B1 - Toe angle adjustment mechanism for vehicle wheels - Google Patents

Toe angle adjustment mechanism for vehicle wheels Download PDF

Info

Publication number
EP0827893B1
EP0827893B1 EP97115260A EP97115260A EP0827893B1 EP 0827893 B1 EP0827893 B1 EP 0827893B1 EP 97115260 A EP97115260 A EP 97115260A EP 97115260 A EP97115260 A EP 97115260A EP 0827893 B1 EP0827893 B1 EP 0827893B1
Authority
EP
European Patent Office
Prior art keywords
steering
distal end
coupling pin
wheel
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97115260A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0827893A3 (en
EP0827893A2 (en
Inventor
Yoshihisa Iwanaga
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP0827893A2 publication Critical patent/EP0827893A2/en
Publication of EP0827893A3 publication Critical patent/EP0827893A3/en
Application granted granted Critical
Publication of EP0827893B1 publication Critical patent/EP0827893B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D17/00—Means on vehicles for adjusting camber, castor, or toe-in

Definitions

  • the present invention relates to toe angle adjustment mechanisms that facilitate toe-in and toe-out adjustment of vehicle wheels.
  • a typical FHPS type rear axle includes a rear axle beam 1.
  • a wheel 2 is coupled to each end of the axle beam 1.
  • a cylinder 5 is fixed longitudinally to the middle of the axle beam 1.
  • a piston rod 4 extends outward from each end of the cylinder 5. The projection and retraction of the piston rod 4 turns each wheel 2 about an axis extending in a substantially vertical direction. This steers the vehicle.
  • Each wheel 2 is coupled to the axle beam 1 by means of a steering knuckle 3.
  • the steering knuckle 3 is turned accordingly.
  • the steering knuckle 3 is connected to the piston rod 4 by means of a rod end 7, which is secured to the distal end of the piston rod 4, a tie rod 18, and a ball joint.
  • the cylinder 5 is actuated by hydraulic pressure.
  • the hydraulic pressure is applied by a steering valve, or ORBITROL, located below a steering wheel (not shown), which is arranged in front of the driver's seat.
  • a nut portion 7a is provided on each rod end 7. The rod end 7 is threaded into the piston rod 4. The length of the piston rod 4 is adjusted by rotating the nut portion 7a.
  • each rod end 7 is turned to adjust the length of the piston rod 4.
  • each rod end 7 must be rotated independently when turning the nut portion 7a.
  • the rod end 7 must be disconnected from the associated tie rod 18 for adjustment.
  • the rod end 7 and the tie rod 18 are reconnected after adjustment.
  • exclusive tools are required to rotate the rod end 7.
  • a steering device which has a steering mechanism for a vehicle, the steering mechanism having a steerable wheel with a steering knuckle coupled to an actuator via a transfer member.
  • the movable connections between these elements are ball joints.
  • document US 4,162,859 shows an adjustable pivot axis which is arranged at the distal end of the steering knuckle so that the steering actuator is directly connected to the steering knuckle.
  • the adjustable pivot axis is embodied as an adjustable ball joint having a frustoconical portion arranged eccentrically with respect to the turning axis of the ball joint.
  • the US 5,213,435 shows an adjustable fastening of a ball joint to a tie rod for steering linkages having a mechanism for pivoting the axis of the ball joint relatively to a centre axis.
  • the adjustment movement is generated with a screw using the threaded portion thereof as a drive co-operating with a suitable gearing provided on a fastening plate.
  • the fastening plate is fixed in the adjusted position by means of clamping screws.
  • Figs. 1(a) and 1(b) show a rear axle of a forklift.
  • the rear axle includes a laterally extending rear axle beam 1, or frame member, which is fixed to the rear portion of the vehicle body.
  • a wheel 2 is coupled to each end of the axle beam 1 by means of a steering knuckle 3.
  • Each wheel 2 rotates about a horizontal axis and pivots about a vertical axis.
  • a single piston rod 4 extends outward from each end of the cylinder 5.
  • a rod end 7 is integrally fixed to each end of the piston rod 4.
  • the cylinder 5 is actuated by hydraulic pressure. The hydraulic pressure is applied by a steering valve, or ORBITROL, located below a steering wheel (not shown), which is arranged in front of the driver's seat.
  • a connecting portion 8 which is bifurcated into a first connecting piece 8a and a second connecting piece 8c, is provided at the distal end of the rod end 7.
  • a slot 8b which is slightly wider than the thickness of a tie rod 18, is defined between the first and second connecting pieces 8a, 8c.
  • a first bore 9 extends through the first connecting piece 8a, while a second bore 10 extends through the second connecting piece 8c.
  • a lock plate 12 having a hexagonal hole 11, which constitutes part of a rotation restricting mechanism, is fastened to the outer surface of the first connecting piece 8a by a bolt 12a.
  • the first bore 9, the second bore 10, and the hexagonal hole 11 are aligned coaxially.
  • the diameter of the first bore 9 is greater than that of the second bore 10.
  • a coupling pin 13 has first and second sections 14, 15 that correspond to the bores 9, 10, respectively, and a head 16 corresponding to the hexagonal hole 11.
  • An eccentric section 17 extends between the first and second sections 14, 15. The outer surface of the eccentric section 17 is spherical.
  • the tie rod 18 connects the steering knuckle 3 to the piston rod 4.
  • a pin bore 18a is provided on the end of the tie rod 18.
  • the tie rod 18 and the steering knuckle 3 are rotatably coupled to each other by a known coupling device.
  • the rod end 7 is connected to the tie rod 18 in the following manner. As shown in Fig. 3, the distal end of the tie rod 18 is fit into the slot 8b.
  • the pin bore 18a is located between the first bore 9 and the second bore 10.
  • the coupling pin 13 is then inserted through the first bore 9, the pin bore 18a, and the second bore 10.
  • a lock pin 19 is used to lock the projecting lower end of the coupling pin 13. Since the slot 8b is slightly wider than the thickness of the tie rod 18, a slight clearance is formed between the tie rod 18 and the walls of the slot 8b.
  • a sleeve 20 is arranged between the eccentric section 17 of the coupling pin 13 and the wall of the pin bore 18a.
  • the sleeve 20 is not necessary if the eccentric section 17 can easily slide against the pin bore 18a without undue wear.
  • the spherical surface of the eccentric section 17 contacts the wall of the pin bore 18a by means of the sleeve 20.
  • the tie rod 18 pivots about the eccentric section 17 of the connecting pin 13 in accordance with the movement of the rod end 7.
  • the eccentric shaft portion 17 functions in the same manner as a ball joint.
  • the center of the eccentric section 17 is offset from the axis of the coupling pin 13 by a predetermined distance.
  • the center of the eccentric section 17 orbits the axis of the pin 13.
  • the locus of the center of the eccentric section 17 defines a circle, the radius of which is equal to the offset distance.
  • the head 16 of the coupling pin 13 is fitted into the hexagonal hole 11 so as to restrict rotation of the pin 13.
  • the coupling pin 13 may be moved upward until the head 16 comes out of the hexagonal hole 11. This enables the head 16 to be turned in increments of 60 degrees.
  • the angular interval of 60 degrees allows alignment between the outer surface of the head 16 and the wall of the hexagonal hole 11.
  • the turning of the coupling pin 13 changes the position at which the tie rod 18 is connected to the rod end 7 in the axial direction of the cylinder 5. This adjusts the toe angle of the wheel.
  • the hexagonal head of the coupling pin is aligned with and fit into the hexagonal hole that is provided in the lock plate so as to restrict rotation of the coupling pin.
  • the portion of engagement between the coupling pin and the lock plate need not be hexagonal as long as it is polygonal.
  • the lock plate may be eliminated by providing a polygonal hole in the rod end.
  • the rotation restricting means is not limited to a polygonal engagement mechanism and may employ other restricting mechanisms. When using polygonal engagement mechanisms, it is preferable that the number of sides be as high as possible to allow fine adjustment.
  • a slot is provided in the rod end.
  • the slot may instead be provided in the tie rod.
  • the lock plate is also arranged on the tie rod.
  • the eccentric section does not necessarily have to be provided at the middle of the coupling pin and may be provided at any position on the pin.
  • the outer surface of the eccentric section need not be spherical and may be cylindrical. However, in this case, a separate ball joint will be necessary. Thus, such structure may not be cost efficient.
  • the lock plate 12 and the coupling pin 13 do not necessarily have to be arranged on the upper surface of the rod end 7 and may be arranged on the lower surface instead.
  • the toe angle adjustment mechanism may be employed anywhere as long as it defines a rotatable joint with a member that is mechanically connected to the steering knuckle. This enables the advantageous effects of the above embodiment to be obtained.
  • the application of the present invention is not limited to FHPS type axles and may be applied to vehicles that employ separate type linkage power steering systems. In such a system, the present invention may be applied to portions connecting a pitman arm to a steering connecting rod or to portions connecting a knuckle arm and a tie rod.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
  • Body Structure For Vehicles (AREA)
  • Vehicle Body Suspensions (AREA)
EP97115260A 1996-09-04 1997-09-03 Toe angle adjustment mechanism for vehicle wheels Expired - Lifetime EP0827893B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP23433696 1996-09-04
JP23433696A JP3711649B2 (ja) 1996-09-04 1996-09-04 車輌における車輪のトー角調整機構
JP234336/96 1996-09-04

Publications (3)

Publication Number Publication Date
EP0827893A2 EP0827893A2 (en) 1998-03-11
EP0827893A3 EP0827893A3 (en) 2000-12-20
EP0827893B1 true EP0827893B1 (en) 2003-01-29

Family

ID=16969400

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97115260A Expired - Lifetime EP0827893B1 (en) 1996-09-04 1997-09-03 Toe angle adjustment mechanism for vehicle wheels

Country Status (7)

Country Link
US (1) US6047789A (zh)
EP (1) EP0827893B1 (zh)
JP (1) JP3711649B2 (zh)
KR (1) KR100268316B1 (zh)
CN (1) CN1180632A (zh)
DE (1) DE69718726T2 (zh)
TW (1) TW333506B (zh)

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US6514002B1 (en) * 1998-07-14 2003-02-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Rotary pin
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JP2001097240A (ja) * 1999-09-30 2001-04-10 Toyota Autom Loom Works Ltd 車両における車輪のトー角調整機構及び操舵装置
US6293724B1 (en) * 1999-10-29 2001-09-25 Northstar Manufacturing Co., Inc. Adjustable mount for vehicular ball joints
US6598500B1 (en) 2001-08-20 2003-07-29 Honda Giken Kogyo Kabushiki Kaisha Double-nut tool and method of setting the toe angle of a vehicle wheel
US6561715B2 (en) * 2001-09-19 2003-05-13 American Axle & Manufacturing, Inc. Inner tie rod to relay rod fastening and adjustment system
JP2005104225A (ja) * 2003-09-29 2005-04-21 Aisin Seiki Co Ltd アライメント制御装置
US7398982B2 (en) * 2004-03-12 2008-07-15 Honda Motor Co., Ltd. Suspension device
KR100610110B1 (ko) * 2004-09-06 2006-08-10 기아자동차주식회사 자동토우조절 기능을 갖는 서스펜션 시스템
KR100622004B1 (ko) * 2005-06-14 2006-09-08 현대모비스 주식회사 차량 현가의 토우를 조절하는 장치의 구조
KR100621913B1 (ko) 2005-08-26 2006-09-08 현대자동차주식회사 차량용 프론트 액슬 토우인 조정장치
DE102005046895A1 (de) * 2005-09-30 2007-05-03 Zf Friedrichshafen Ag Achsschenkellenkvorrichtung eines Fahrzeugs
US7618047B2 (en) * 2005-12-02 2009-11-17 Ford Global Technologies, Llc Automobile steering linkage systems and methods
KR100756848B1 (ko) * 2006-05-25 2007-09-07 주식회사 만도 자동차의 후륜 토우각 제어장치
JP5098242B2 (ja) * 2006-07-26 2012-12-12 アイシン精機株式会社 車輪操舵装置
US20080240847A1 (en) * 2007-04-02 2008-10-02 Stephen Kent Crouse Eccentric Mount Ball Stud For Steering Toe Adjustment
JP4389993B2 (ja) * 2007-11-22 2009-12-24 トヨタ自動車株式会社 車両のステアリング装置
DE102009006903A1 (de) * 2009-01-30 2010-08-05 Audi Ag Vorrichtung zum Verstellen von Sturz und/oder Spur der Räder von Radaufhängungen
DE102009021477A1 (de) * 2009-05-15 2010-11-18 Audi Ag Vorrichtung zum Verstellen von Sturz und/oder Spur
CN101628528B (zh) * 2009-05-15 2011-03-23 邵延 车轮连接结构
KR101090804B1 (ko) * 2009-08-21 2011-12-08 현대자동차주식회사 액티브 지오메트리 컨트롤 서스펜션
JP5578357B2 (ja) * 2010-09-08 2014-08-27 株式会社ジェイテクト 車両用操舵装置
CN101979268B (zh) * 2010-09-25 2012-09-05 合肥工业大学 一种汽车转向轮摆振控制方法
US8480099B2 (en) * 2011-06-13 2013-07-09 Scott S. Porta Apparatus and method for adjusting toe angle in the wheels of a solid axle
JP6076182B2 (ja) * 2013-04-11 2017-02-08 アイシン精機株式会社 金属レバーと金属リンクの金属ピンを介した連結構造
US9409096B2 (en) * 2013-09-10 2016-08-09 Custom Works Rc Products Llc Adjustable toe suspension arm
KR102105512B1 (ko) * 2013-09-11 2020-04-28 주식회사 두산 지게차의 스티어링 액슬 빔 구조
CN105109552A (zh) * 2015-09-10 2015-12-02 力帆实业(集团)股份有限公司 一种汽车前束调节装置
CN107139672B (zh) * 2017-05-27 2023-09-26 北京京安长信科技有限公司 一种可调节的车桥装置
CN107554606B (zh) * 2017-07-14 2023-12-19 浙江工业大学 一种叉车转向机构
US9988083B1 (en) * 2017-07-27 2018-06-05 Justin Smith Tie rod connection pivot assembly
JP6539326B2 (ja) * 2017-10-13 2019-07-03 本田技研工業株式会社 サスペンション装置
US11131337B1 (en) * 2017-11-01 2021-09-28 Northstar Manufacturing Co., Inc. Adjustable ball joint
US11254357B2 (en) * 2018-07-03 2022-02-22 Robby Gordon Offset tie rod joint
CN109050194A (zh) * 2018-08-28 2018-12-21 石海军 机械式主动悬架系统
CN110500938A (zh) * 2019-07-04 2019-11-26 大乘汽车集团有限公司 一种车轮外倾角测量方法及其测量装置
CN111319678A (zh) * 2020-03-23 2020-06-23 淮安信息职业技术学院 悬架结构、汽车以及悬架的外倾角调节方法
US11845316B1 (en) 2021-09-08 2023-12-19 Northstar Manufacturing Co., Inc. Adjustable pivot joint for vehicle suspensions
CN113954582B (zh) * 2021-11-19 2023-08-15 东风华神汽车有限公司 一种浮动桥用自动转向装置及其使用方法、汽车

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Also Published As

Publication number Publication date
DE69718726T2 (de) 2003-09-11
KR19980024190A (ko) 1998-07-06
EP0827893A3 (en) 2000-12-20
CN1180632A (zh) 1998-05-06
JPH1076977A (ja) 1998-03-24
KR100268316B1 (ko) 2000-10-16
DE69718726D1 (de) 2003-03-06
TW333506B (en) 1998-06-11
US6047789A (en) 2000-04-11
JP3711649B2 (ja) 2005-11-02
EP0827893A2 (en) 1998-03-11

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